US11719277B2 - Bearing for a wind turbine, wind turbine comprising a bearing and method for producing a bearing ring - Google Patents

Bearing for a wind turbine, wind turbine comprising a bearing and method for producing a bearing ring Download PDF

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Publication number
US11719277B2
US11719277B2 US17/584,857 US202217584857A US11719277B2 US 11719277 B2 US11719277 B2 US 11719277B2 US 202217584857 A US202217584857 A US 202217584857A US 11719277 B2 US11719277 B2 US 11719277B2
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ring
bearing
bolt
section
bearing according
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US20220260114A1 (en
Inventor
Niels Karl Frydendal
Kim Thomsen
Morten Thorhauge
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Siemens Gamesa Renewable Energy AS
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Siemens Gamesa Renewable Energy AS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/06—Sliding-contact bearings for exclusively rotary movement for axial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D79/00—Methods, machines, or devices not covered elsewhere, for working metal by removal of material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F16C17/035—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings the segments being integrally formed with, or rigidly fixed to, a support-element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
    • F16C32/067—Details of hydrostatic bearings independent of fluid supply or direction of load of bearings adjustable for aligning, positioning, wear or play
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2229/00—Setting preload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/12—Force, load, stress, pressure
    • F16C2240/14—Preload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/12—Force, load, stress, pressure
    • F16C2240/18—Stress
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the following refers to a bearing for a wind turbine, comprising a first and a second ring arranged radially to each other with one ring rotating relative to the other around an axis of rotation, whereby the first ring has a cylindrical ring section and a collar extending radially from the ring section, whereby the collar has an axial support area supporting axial bearing elements.
  • a wind turbine as commonly known, comprises a tower and a nacelle fixed to the top of the tower.
  • a hub to which several rotor blades are attached, is arranged at the nacelle.
  • the hub rotates, when the turbine blades interact with blowing wind and drives a generator for producing electric power, as commonly known.
  • Such a wind turbine comprises several rotating elements, which are arranged in respective bearings.
  • One example is the main bearing of the generator at a direct drive wind turbine, while the turbine may also comprise one or more gears, for example of a planetary gear or a hydraulic gear system.
  • the bearing usually comprises two rings, i.e., a first ring and a second ring which are usually arranged radially to each other.
  • One ring is stationary, while the other ring rotates relative to the first ring.
  • the radially inner ring is stationary and coupled to a stationary main shaft of the wind turbine while the outer ring rotates around the inner ring and is coupled to a rotor of a generator.
  • the outer ring is stationary while the inner ring rotates.
  • the respective rotating ring no matter how the bearing is set up, is coupled to the hub and the respective component which needs to be rotated so that a rotation of the hub is transferred to the component.
  • the bearing is a roller bearing comprising several rollers which may be tapered rollers
  • the bearing is also known to concept the bearing as a sliding bearing or plane bearing.
  • the stationary ring is usually provided with respective bearing elements in form of sliding pads, on which the rotating ring slides and is supported by a very thin fluid film.
  • the bearing pads which may be tiltable and which are therefore able to compensate any geometric tolerances between the rings arising among others from the forces which act on the bearing, are arranged at the stationary ring which has a specific ring design respectively geometry.
  • This ring which may also be named as a housing or a bearing housing, comprises a cylindrical ring section, on which the other ring is radially supported by respective radial bearing elements.
  • the ring is provided with axial bearing elements, which are supported at a specific axial support area realized at this ring.
  • the ring comprises a collar, which extends radially from the cylindrical ring section.
  • the axial ring surface of this collar is the axial support area, at which the sliding bearing elements are supported.
  • An aspect relates to an improved bearing.
  • a bearing as mentioned above is characterized in that several pretension elements creating compressive stress are fixed to the first ring in the section where the collar extends from the ring section.
  • the first ring which comprises the cylindrical ring section and the collar is provided with several pretension elements which are used for creating internal compressive stress in the first ring respectively in the section where the high tensile stress occurs resulting from the axial support of the axial bearing elements respectively the sliding pads.
  • This introduced high compressive stress somehow counteracts the induced tensile stress respectively allow to induce a higher tensile stress until the tolerable tensile stress limit is reached. So, with these pretension elements it is possible to “strengthen” the first ring especially in the section where the high tensile stress is induced, i.e., in the section where the collar extends from the ring section respectively merges with this ring section.
  • the pretension elements are arranged at the first ring in this peculiar section or area where the collar extends from the ring section so that the counteracting compressive stress is generated exactly where it is needed, i.e., at the place where the tensile stress resulting from the operation of the turbine is induced in the first ring.
  • the arrangement of the pretension elements is a cheap but very effective way for enhancing the mechanical properties of the first ring making the ring more tolerable against high tensile stress resulting from respective loads.
  • the first ring respectively the bearing housing material has typically a higher load capacity in view of fatigue and ultimate strength in view of compression loads than in view of tensile loads. Therefore, by the pretension elements the strength of the first ring may significantly be improved.
  • each pretension element is a at least partially threaded bolt inserted in a at least partially threaded bore extending into the ring section, which bolt is directly or indirectly supported on a support surface against the ring.
  • It may be a bolt-nut-combination with the nut being screwed on the bolt and which nut is supported against the respective support surface which may either be directly provided at the ring or by a washer or the like.
  • bolts having a hex head may be used which is directly supported on the ring support surface or at a respective intermediate washer or the like.
  • the bores in which the bolts are inserted respectively screwed are provided in an axial surface of the first ring and extend into the ring section.
  • the bores are provided at the outer axial ring surface of the first ring and run into the cylindrical ring section.
  • the length of the bore depends on the thickness of the collar, seen in the axial direction, as the bore needs to extend quite deep into this ring section, over at least one third of the axial thickness respectively about half of its axial thickness.
  • the bores and the bolts are arranged around the axis of rotation of the bearing in an equidistant distribution.
  • a respective number of bolts and bores are provided, for example any number between 10-30 bores respectively bolts, depending on the diameter of the ring. In an embodiment, the number is between 15-25, and between 18-22.
  • each bore and certainly also the respective bolt extends parallel to the axis of rotation of the bearing.
  • each bore, and the respective bolt extend under an angle to the axis of rotation into the ring section. The orientation depends on the orientation of the collar. If the collar extends radially outward from the cylindrical ring section, the bores and bolts are orientated towards the axis of rotation. If the collar extends inward, the longitudinal axis of the bores and bolts run away from the axis of rotation.
  • the angle is between 3°-30°, between 5°-20°.
  • the chosen angle certainly depends on the final geometry of the first ring in this area.
  • the bolt as mentioned is at least partially threaded at least at one end, which end is inserted in the threaded bore which may either be threaded over its whole length, or only in its inner end region. It is certainly possible that the bolt is also threaded over its whole length.
  • each bolt may extend with a threaded end out or the bore, whereby a nut is screwed on the thread, which nut is supported on the support surface.
  • the bolt is a simple threaded stud which stud may be threaded over its whole length or only in the respective end regions, with one end region being screwed into the bore thread. The other end extends out of the bore.
  • a nut is screwed on this end, which nut is firmly screwed against the respective support surface thereby tensioning the bolt respectively stud and with this the first ring. The tension may be appropriately adjusted by the torque applied to the nut.
  • each bolt has a bolt head comprising an attachment section for a tool, which bolt head is supported on the support surface.
  • the bolt may be provided for example with a hex head.
  • the bolt is threaded at its opposite end section or over its whole length and screwed into the bore thread until the bolt head is supported on the support surface. Also here, depending on the torque applied to the bolt head, the tension of the bolt and therefore the applied compressive stress may be adjusted appropriately.
  • a further embodiment of the invention provides that the nut or the bold head of each bolt arranged angled towards the axis of rotation is supported on a support surface which is orientated perpendicular to the longitudinal bore axis. This embodiment allows for a perfect even or symmetrical load distribution of the load applied by the nut respectively the bolt head to the support surface. Both, the nut and the bolt head have a flat contact surface.
  • this angle is compensated by also arranging the support surface in a respective angled position.
  • the support surface is orientated perpendicular to the longitudinal bore axis and is therefore parallel to the respective contact surface of the nut respectively the bolt head. This ascertains that the nut or the bolt head contact surface is completely supported on the respective support surface, so that any load is evenly distributed over this contact area.
  • the respective support surface may be integral with the first ring.
  • the ring is machined at its axial front surface, where the nut or the bolt head shall be supported, in order to work out the respective ring-shaped areas with the angled support surfaces.
  • the support surface can be provided with an excellent orientation.
  • a respective washer comprising the support surface.
  • the axial ring surface is flat.
  • a washer is attached to this ring surface, through which the bolt is inserted into the bore.
  • the washer itself comprises the respective angled support surface.
  • the orientation of the washer around the bore axis needs to be adjusted in order to have a flat overall contact of the contact surface of the nut or the bolt head on the respective washer support surface. Nevertheless, also this embodiment allows for an excellent load distribution.
  • the bearing elements supported at the first ring respectively fixed there to at the collar are tiltable fluid film bearing pads, on which the second ring, which has for example a rectangular cross-section, is axially supported. So, the bearing itself is a fluid film bearing respectively a sliding bearing.
  • Embodiments of the invention further refer to a wind turbine which comprises at least one bearing as previously mentioned. This bearing is the main bearing of the turbine.
  • the first ring is an inner ring and is coupled to a stationary shaft, while the second ring is an outer ring and is coupled to a rotor of a generator.
  • embodiments of the invention also refer to a method for producing a first ring of a bearing as previously mentioned.
  • This method is characterized in that the pretension elements are first fixed to the ring and tensioned for generating the compression stress, whereafter the support area of the collar is machined.
  • This inventive method addresses the fact, that in a fluid film bearing using respective tilting sliding pads it is important to have highly accurate machined surfaces at the respective first ring respectively the bearing housing, on which surfaces the individual sliding pads rest. This means that the support surface of the collar needs to be perfectly machined in order to ensure a most even load distribution between the sliding pads.
  • the pretension elements, respectively the bolts are tensioned, the first ring respectively the bearing housing will slightly deform resulting in a slightly uneven support surface provided at the collar.
  • the inventive method proposes to first fix and tension all pretension elements and to generate the requested and well-defined compression stress, which fixation results in the mentioned slight deformation of the support surface. After all pretension elements are tensioned, the respective collar support surface is machined in order to ascertain, that this support surface is completely flat in order to support all sliding pads perfectly.
  • FIG. 1 shows a principle perspective illustration of a wind turbine
  • FIG. 2 shows a partial view in cross-section of the hub, the main shaft and the generator comprising a respective inventive bearing
  • FIG. 3 shows a cross-section of an inventive bearing in an area, where no pretension element is provided, for illustrating the induced tensile stress
  • FIG. 4 shows a perspective cross-section of the inventive bearing in the area where the pretension element angled to the axis of rotation is provided;
  • FIG. 5 shows a perspective view of an inventive bearing from the side where the pretension elements are arranged
  • FIG. 6 shows a principle cross-section illustration with a pretension element arranged in parallel to the axis of rotation.
  • FIG. 1 shows a principle illustration of a wind turbine 1 comprising a rotor 2 , a nacelle 3 and a tower 4 , on top of which the nacelle 3 is arranged.
  • the rotor 2 comprises three rotor blades 5 which are attached to a hub 6 .
  • the principle setup of such a wind turbine is known.
  • the wind turbine 1 comprises a stationary main shaft 7 , which is connected to a main bearing 8 .
  • This main bearing 8 comprises an inner or first ring 9 , which is stationary and connected to the stationary main shaft 7 .
  • the bearing 8 further comprises a radially outer or second ring 10 , which rotates relative to the stationary first ring 9 around the bearing axis of rotation.
  • the hub 6 is connected so that a rotation of the hub 6 causes a rotation of the second ring 10 .
  • To this second ring 10 furthermore the rotor 11 of a generator 12 is connected, so that this rotor 11 is rotated when the hub 6 rotates.
  • the generator 12 further comprises a stator 13 , which is stationary connected to the stationary shaft 7 . Also, this setup of a direct drive wind turbine 1 is commonly known.
  • FIG. 3 shows a cross-section of the bearing 8 . It shows the inner first ring 9 and the outer second ring 10 .
  • the bearing 8 itself is a fluid film slide bearing in which the rotatable outer second ring 10 is radially and axially guided on the stationary inner second ring 9 by respective radial and axial bearing elements in form of sliding pads and a fluid film provided between the second ring 10 respectively its sliding surfaces and the respective sliding pads.
  • FIG. 3 shows only the axial sliding pads 14 at the inner bearing side, which is orientated towards the main shaft 7 and the sliding pads 15 at the outer side of the bearing 8 are shown.
  • the bearing elements in form of the sliding pads 15 are tiltable elements which, as shown at the sliding pad 15 .
  • a mounting base 16 is provided by which each sliding pad is mounted respectively supported at the first ring 9 , to which mounting base 16 the sliding pad 15 guiding the respective ring is attached by a ball joint 17 allowing the sliding pad 15 to slightly tilt relative to the mounting base 16 .
  • the sliding pad 15 has a flat sliding surface 18 while the second ring 10 has a flat axial sliding surface 19 which slide on the sliding surface 18 by an intermediate fluid film 20 . The same is true for the sliding pad 14 .
  • the first ring 9 has a specific L-shaped cross-section design. It comprises a cylindrical ring section 21 , to which several radial slide bearing pads, which are not shown, are attached on which the second ring 10 is radially guided. Also here, a respective fluid film slide bearing contact is realized. From this cylindrical ring section 21 , a collar 22 extends radially to the outside of the ring 9 , as FIG. 3 shows.
  • This collar which is provided at the axial end of the ring 9 , is provided with an axial support area 23 , which is a flat ring support surface, at which the respective flat contact surface 24 of the mounting base 16 is supported respective to which it is fixed. So, obviously the cylindrical ring section 21 and the collar 22 form a L-shaped cross-section.
  • the axial sliding pads 15 exert an axial force on the support area 23 and thus on the collar 22 .
  • the double arrows P 2 are vectors showing the tensile stress in the material respectively the area of the first ring 9 where this high tensile stress is given. This high tensile stress is problematic with respect to the structural integrity of the first ring 9 respectively the whole fluid film bearing 8 in view of fatigue and extreme loads.
  • the first ring 9 is provided with several bores 26 , which extend from the outer axial front surface 27 of the ring 9 respectively the ring section 21 into the ring section 21 , as shown in FIG. 4 .
  • the bore 26 is provided with a thread 28 at least at its inner end or over its complete length.
  • a bolt 29 is screwed into this threaded bore 26 .
  • the bolt 29 comprises at least a thread 30 at its inner end which is screwed into the thread 28 of the bore 26 .
  • the opposite end of the bolt 29 extends out of the bore 26 and is also provided with a thread 31 .
  • This flat support surface 34 is integrally provided at the ring 9 respectively at the axial front surface 27 as shown in FIG. 5 .
  • the longitudinal axis of the bore 26 and therefore also the longitudinal axis of the bolt 29 is angled relative to the axis of rotation of the bearing.
  • the angle ⁇ is shown in FIG. 4 .
  • the support surface 34 is respectively angled. It is perpendicular to the longitudinal axis of the bore 26 respectively the bolt 29 , corresponding to the respective angled arrangement of the bore 26 respectively the bolt 29 . This allows for a very even load distribution.
  • FIG. 6 shows another embodiment of the first ring 9 comprising the cylindrical ring section 21 and the collar 22 .
  • axial bearing elements 15 respectively sliding pads are axially supported on the collar 22 in the same manner as described to FIG. 3 .
  • the pretension elements 26 are provided at the first ring 9 .
  • the first ring 9 is provided with a respective number of threaded bores 26 .
  • a bolt 29 is screwed into each bore 26 .
  • the bolt 29 comprises an integral bolt head 35 , here in form of a hex head, allowing a tool to be engaged at the bolt head 35 .
  • a washer 36 is arranged, which provides a respective support surface 37 on which the respective contact surface 38 of the bolt head 35 is supported.
  • the longitudinal axis of the bore 26 and therefore of the bolt 29 is parallel to the axis of rotation.
  • a number of pretension elements 25 is provided around the circumference of the first ring 9 in an even respectively equidistant distribution, as shown in FIG. 5 .
  • the number of pretension elements 25 is selected depending on the expected tensile stress respectively loads which need to be compensated.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Optics & Photonics (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Wind Motors (AREA)
  • Sliding-Contact Bearings (AREA)
US17/584,857 2021-02-12 2022-01-26 Bearing for a wind turbine, wind turbine comprising a bearing and method for producing a bearing ring Active US11719277B2 (en)

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TW202237976A (zh) 2022-10-01
JP2022123867A (ja) 2022-08-24
CN114922907B (zh) 2025-06-24
EP4043743A1 (de) 2022-08-17
EP4043743B1 (de) 2023-10-04
CN114922907A (zh) 2022-08-19
TWI802240B (zh) 2023-05-11
JP7326512B2 (ja) 2023-08-15
DK4043743T3 (da) 2023-11-20
US20220260114A1 (en) 2022-08-18

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